CN106917817B

CN106917817B - Tapered roller bearing

Info

Publication number: CN106917817B
Application number: CN201611165878.6A
Authority: CN
Inventors: 铃木章之
Original assignee: JTEKT Corp
Current assignee: JTEKT Corp
Priority date: 2015-12-17
Filing date: 2016-12-16
Publication date: 2020-06-09
Anticipated expiration: 2036-12-16
Also published as: CN106917817A; JP2017116089A; JP6729117B2

Abstract

The invention provides a tapered roller bearing. The tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers, and a lubricant retaining member. A first raceway surface is formed on an inner peripheral surface of the outer ring. The inner ring is disposed on the same shaft as the outer ring. A second raceway surface is formed on the outer peripheral surface of the inner ring. The plurality of tapered rollers are disposed between the first raceway surface and the second raceway surface, and are arranged in the circumferential direction of the outer ring. The lubricant retaining member is provided integrally with the outer ring. The lubricant retaining member includes a cylindrical portion and an annular portion. The cylindrical portion extends in the axial direction of the outer ring. The cylindrical portion is located at one axial end of the outer ring. The annular portion extends inward in the radial direction of the outer ring from one end of the cylindrical portion in the axial direction. The plurality of recesses are formed in the inner circumferential surface of the cylindrical portion in a circumferentially aligned manner.

Description

Tapered roller bearing

The disclosures of Japanese patent application 2015-24961, 12/17 in 2015 and Japanese patent application 2016-139972, 2016, 7/15, including the description, drawings and abstract thereof, are incorporated herein by reference in their entirety.

Technical Field

The present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing in which lubricating oil is supplied to a space in which tapered rollers rotate.

Background

The tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers, and a retainer. The tapered rollers are arranged such that their central axes are inclined with respect to the central axis of the tapered roller bearing. At least a part of the large diameter end surface (hereinafter referred to as a large end surface) of the tapered roller is positioned radially outward of the bearing than the small diameter end surface (hereinafter referred to as a small end surface).

As characteristics of the tapered roller bearing, for example, it is required to: (1) improving the resistance to fusing of the large end face of the tapered roller and a surface (hereinafter referred to as a large flange surface) of the inner ring that is in contact with the large end face of the tapered roller; and (2) suppressing wear of the tapered rollers and pocket surfaces of the cage (inner surfaces of pockets formed in the cage and accommodating the tapered rollers). As such a tapered roller bearing, a tapered roller bearing is known in which a lubricant retaining member is attached to an outer ring and lubricant is retained in a space between the lubricant retaining member and the outer ring (for example, japanese patent application laid-open No. 2008-057791).

Foreign matter such as dust from the outside and abrasion powder of the tapered roller may be mixed into the lubricating oil. If the lubricating oil containing these foreign matters enters between the tapered rollers and the raceway surface, abnormal noise may be generated by the foreign matters when one of the inner ring and the outer ring of the tapered roller bearing rotates relative to the other, or the bearing life may be reduced.

Disclosure of Invention

One of the objects of the present invention is to suppress the occurrence of abnormal noise when one of an inner ring and an outer ring of a bearing rotates relative to the other, which is caused by foreign matter contained in lubricating oil, and to suppress the reduction in the life of the bearing.

A tapered roller bearing according to an aspect of the present invention is characterized by comprising an outer ring, an inner ring, a plurality of tapered rollers, and a lubricant retaining member. A first raceway surface is formed on an inner peripheral surface of the outer ring. The inner ring is disposed on the same shaft as the outer ring. A second raceway surface is formed on the outer peripheral surface of the inner ring. The plurality of tapered rollers are disposed in a space formed between the first raceway surface and the second raceway surface. The plurality of tapered rollers are arranged in the circumferential direction of the outer ring. The lubricant retaining member is provided integrally with the outer ring. The lubricant retaining member includes a cylindrical portion and an annular portion. The cylindrical portion extends in the axial direction of the outer ring. The cylindrical portion is located at one axial end of the outer ring. The annular portion extends inward in the radial direction of the outer ring from one end of the cylindrical portion in the axial direction. The plurality of recesses are formed in the inner circumferential surface of the cylindrical portion in a circumferentially aligned manner.

Drawings

The foregoing and other features and advantages of the invention will be apparent from the following description of the preferred embodiments, as illustrated in the accompanying drawings in which like reference characters refer to the same parts throughout the several views.

Fig. 1 is a sectional view showing the entire tapered roller bearing according to embodiment 1.

Fig. 2 is a sectional view of a tapered roller bearing according to embodiment 1.

Fig. 3 is a perspective view of the holder.

Fig. 4 is a sectional view of a tapered roller bearing according to embodiment 1.

Fig. 5 is a perspective view of the ring.

Fig. 6 is a sectional view of a tapered roller bearing according to embodiment 1.

Fig. 7 is an explanatory view showing a part of the tapered roller bearing from the axial front side, in which a lubricating oil is accumulated.

Fig. 8 is a perspective view of a ring in a modification of embodiment 1.

Fig. 9 is an enlarged cross-sectional view of a part of the tapered roller bearing according to embodiment 2.

Fig. 10 is an enlarged cross-sectional view of a part of a tapered roller bearing according to embodiment 3.

Fig. 11 is an enlarged cross-sectional view of a part of a tapered roller bearing according to variation 1 of embodiment 3.

Fig. 12 is an enlarged cross-sectional view of a part of a tapered roller bearing according to variation 2 of embodiment 3.

Fig. 13 is an enlarged cross-sectional view of a part of a tapered roller bearing according to embodiment 4.

Detailed Description

A tapered roller bearing according to an embodiment of the present invention includes an outer ring, an inner ring, a plurality of tapered rollers, and a lubricant retaining member. A first raceway surface is formed on an inner peripheral surface of the outer ring. The inner ring is disposed on the same shaft as the outer ring. A second raceway surface is formed on the outer peripheral surface of the inner ring. The plurality of tapered rollers are disposed in a space formed between the first raceway surface and the second raceway surface. The plurality of tapered rollers are arranged in the circumferential direction of the outer ring. The lubricant retaining member is provided integrally with the outer ring. The lubricant retaining member includes a cylindrical portion and an annular portion. The cylindrical portion extends in the axial direction of the outer ring. The cylindrical portion is located at one axial end of the outer ring. The annular portion extends inward in the radial direction of the outer ring from one end of the cylindrical portion in the axial direction. The plurality of recesses are formed in the inner circumferential surface of the cylindrical portion in a circumferentially aligned manner.

In the tapered roller bearing, the lubricant is held in a space formed between the outer ring and the lubricant holding member. According to the tapered roller bearing, a plurality of concave portions are formed in the inner peripheral surface of the cylindrical portion of the lubricant retaining member. Therefore, when foreign matter such as dust from the outside and abrasion powder of the tapered rollers is mixed into the lubricating oil, the foreign matter that moves due to the flow of the lubricating oil generated when one of the inner ring and the outer ring rotates relative to the other enters the recess. As a result, foreign matter is prevented from being caught between the tapered roller and the outer ring or between the tapered roller and the inner ring. Therefore, the occurrence of abnormal noise and the reduction in the bearing life can be suppressed when one of the inner ring and the outer ring rotates relative to the other.

The aspect in which the cylindrical portion is located at the one end portion in the axial direction of the outer ring includes not only (1) the aspect in which the cylindrical portion is realized by the one end portion in the axial direction of the outer ring itself, but also (2) the aspect in which the cylindrical portion is realized by a member that includes the one end portion in the axial direction of the outer ring and is provided separately from the outer ring, and (3) the aspect in which the cylindrical portion is realized by the member itself that is fixed to the one end portion in the axial direction of the outer ring and is provided separately from the outer.

The cylindrical portion may be formed separately from the outer ring. In this case, the concave portion is easily formed in the cylindrical portion.

The outer race also includes a thin-walled cylindrical portion. The thin-walled cylinder portion is formed at one axial end of the outer ring by an annular step provided on the inner peripheral surface of the outer ring. The thin-walled cylinder portion extends in the axial direction. The cylindrical portion includes a thin-walled cylindrical portion and an inner cylindrical portion. One end of the inner cylindrical portion in the axial direction is connected to the outer peripheral edge of the annular portion. The outer peripheral surface of the inner cylindrical portion is in contact with the inner peripheral surface of the thin-walled cylindrical portion in the radial direction. The inner cylindrical portion is formed with a plurality of notches or holes arranged in the circumferential direction. In this case, a plurality of recesses are realized including a plurality of notches or holes.

Preferably, each of the plurality of recesses has a substantially rectangular shape when viewed in a radial direction of the outer ring. In each of the plurality of recesses, a length in the axial direction is larger than a length in the circumferential direction. In this case, the recessed portion can be easily formed regardless of whether the cylindrical portion is formed of metal or synthetic resin.

According to the above configuration, the recess is formed in a substantially rectangular shape having a longitudinal direction in the axial direction with respect to the flow direction of the lubricating oil in the circumferential direction. This can prevent foreign matter that has entered the recess from flowing out of the recess via the lubricating oil. Therefore, the occurrence of abnormal noise and the reduction in the life of the bearing when one of the inner ring and the outer ring of the bearing rotates relative to the other can be more effectively suppressed.

The plurality of recesses are preferably formed at equal intervals in the circumferential direction. In this case, the number of the plurality of concave portions is preferably n or more satisfying the following expression (1).

In formula (1), n is an integer, and θ is an angle satisfying cos θ ═ R/R. Wherein R is a radius of an inner peripheral surface of the cylindrical portion, and R is a radius of an inner peripheral edge of the annular portion.

According to the above configuration, at least 1 recessed portion is present in the portion of the cylindrical portion where the lubricating oil is accumulated. This allows foreign matter contained in the lubricating oil to be efficiently accommodated in the recess.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the following description, for convenience of explanation, the drawings referred to simply show, in simplified form, only the main components necessary for explaining the present invention among the constituent components of the embodiment of the present invention. Therefore, the present invention may include any constituent member not shown in the following figures. The dimensions of the members in the drawings below do not faithfully represent actual dimensions, dimensional ratios of the members, and the like.

Fig. 1 is a sectional view of a tapered roller bearing 1 according to embodiment 1. Fig. 1 is a sectional view through a center axis L1 of the tapered roller bearing 1. The tapered roller bearing 1 is used for a bearing device for a drive wheel of a vehicle such as an automobile. In the present specification, the term "axial" is used to indicate the axial direction of the central axis L1.

As shown in fig. 1, the tapered roller bearing 1 includes an outer ring 10, an inner ring 20, a plurality of tapered rollers 30, a retainer 40, and a retaining member 50. The outer ring 10, the inner ring 20, the retainer 40, and the retaining member 50 are annular members provided on the same shaft as the central axis L1 of the tapered roller bearing 1.

As shown in fig. 1, the outer ring 10 and the inner ring 20 are arranged such that the inner ring 20 is fitted to the radially inner side of the outer ring 10. The cage 40 is disposed in a space radially sandwiched by the outer ring 10 and the inner ring 20. The plurality of tapered rollers 30 are held by a retainer 40. The holding member 50 is attached to one end of the outer ring 10 in the axial direction.

The tapered roller 30 has a truncated cone shape. The center axis L2 of the tapered roller 30 is inclined with respect to the center axis L1. The central axis L2 is separated from the central axis L1 from the end face 31 on the small diameter side (hereinafter referred to as the small end face 31) of the tapered roller 30 toward the end face 32 on the large diameter side (hereinafter referred to as the large end face 32).

In the following description of the present specification, the direction of the tapered roller 30 on the small end surface 31 side in the axial direction is referred to as the "small diameter side", and the direction on the large end surface 32 side is referred to as the "large diameter side".

Fig. 2 is an enlarged cross-sectional view of a part of the tapered roller bearing 1.

The outer ring 10 has a first raceway surface 11 on an inner peripheral surface. The first raceway surface 11 has a tapered shape in which the distance from the central axis L1 increases from the small diameter side toward the large diameter side.

An annular step 15 is formed in the circumferential direction on the inner circumferential surface of the outer ring 10. The step 15 is formed on the larger diameter side than the axial center portion of the outer ring 10. The outer ring 10 has a thin cylindrical portion 16 radially outward of the step 15 and having a smaller thickness than the radially inward portion. The step 15 and the thin cylindrical portion 16 are formed to fit the holding member 50 to the outer ring 10.

As shown in fig. 2, the inner race 20 has a second raceway surface 22 on the outer peripheral surface. The second track surface 22 has a tapered shape in which the distance from the central axis L1 increases from the small diameter side toward the large diameter side. The taper angle of the second raceway surface 22 is smaller than the taper angle of the first raceway surface 11.

The inner race 20 has a radial dimension on the smaller diameter side than the second raceway surface 22, and is formed with a small flange portion 25 that is larger than the second raceway surface 22 and faces the small end surface 31 of the tapered roller 30. The large flange portion 26, which has a radial size larger than the second raceway surface 22 on the larger diameter side than the second raceway surface 22 and faces the large end surface 32 of the tapered roller 30, is formed larger than the second raceway surface 22.

As shown in fig. 2, the tapered roller 30 is disposed in a space formed between the first raceway surface 11 and the second raceway surface 22. As described above, each of the plurality of tapered rollers 30 has a shape of a truncated cone, and the central axis L2 is inclined with respect to the central axis L1.

Fig. 3 is a perspective view of the holder 40. As shown in fig. 3, the retainer 40 has an annular shape having a tapered surface whose distance from the central axis L1 increases from the small diameter side toward the large diameter side. A plurality of pockets 41 are formed in the tapered surface of the retainer 40. Each of the plurality of pockets 41 in the tapered surface has a substantially truncated cone shape corresponding to the shape of the tapered roller 30. The holder 40 is formed of metal or resin.

Fig. 4 is a sectional view of the tapered roller bearing 1 showing the retaining member 50 and a part of the outer ring 10. As shown in fig. 4, the holding member 50 is composed of a ring 60 and an elastomer lip 70.

The ring 60 includes a cylindrical ring body 61, and annular claws 62 protruding radially inward from the inner peripheral surface of the ring body 61. The ring body 61 and the claws 62 are integrally formed. The outer diameter of the ring main body 61 is sized to be press-fitted into the inner circumferential surface of the thin-walled tube portion 16 of the outer ring 10. The claws 62 are formed on the axially outer side of the ring body 61. The ring 60 is made of metal such as stainless steel. The detailed configuration of the ring 60 will be described later.

The shape of the elastomer lip 70 as a whole is a circular ring shape. The radially outward portion of the elastic body lip 70 is a thick portion 71, and the thickness in the axial direction is larger than the thickness of the claw 62 of the ring 60. The radially inner portion of the elastic body lip 70 is a thin portion 72, and the thickness in the axial direction is smaller than that of the thick portion 71. The elastomer lip 70 is formed of rubber such as nitrile rubber, acrylic rubber, or the like.

In the elastic body lip 70, a thick portion 71 and a thin portion 72 are formed continuously and integrally. That is, on the axially inner surface of the elastic lip 70, the surface 71b of the thick portion 71 is located axially inward of the surface 72b of the thin portion 72.

The thick portion 71 is formed with a groove 73 extending radially from the outside to the inside. The groove 73 is formed over the entire circumference of the thick portion 71. The groove 73 is sized to fit the claw 62 of the ring 60. By fitting the claws 62 into the grooves 73, the ring 60 and the elastomer lip 70 are integrally combined, constituting the holding member 50.

The ring 60 and the elastic body lip 70 are integrally combined, so that the annular portion 51 and the cylindrical portion 52 of the holding member 50 are integrally formed. The annular portion 51 corresponds to the claws 62 and the elastomer lip 70 of the ring 60. The cylindrical portion 52 corresponds to the ring main body 61.

As shown in fig. 4, the ring 60 is fitted into the large-diameter-side end portion of the outer ring 10 so that the outer peripheral surface thereof contacts the inner peripheral surface of the thin-walled tube portion 16 of the outer ring 10 in the radial direction. Thereby, the outer ring 10 and the holding member 50 are fixed integrally.

As shown in fig. 4, the space formed between the holding member 50 and the outer ring 10 accommodates lubricating oil. The lubricating oil is accumulated in the lower portion of the tapered roller bearing 1 (see fig. 1). The height of the lubricant liquid surface S1 is substantially the same as the height of the lowermost elastic body lip 70 of the tapered roller bearing 1.

In the stationary state of the tapered roller bearing 1, the lubricating oil contacts a part of the outer ring 10, a part of the tapered rollers 30, and a part of the retainer 40. By the rotation of the tapered roller bearing 1, the lubricating oil accumulated in the lower portion of the tapered roller bearing 1 is wound up while rotating. Thereby, the lubricant is supplied to the first raceway surface 11, the second raceway surface 22, and the like. Further, the friction generated between the tapered roller 30 and the first raceway surface 11, between the tapered roller 30 and the second raceway surface 22, and the like is reduced by the supplied lubricating oil.

The ring 60 will be described in detail below. Fig. 5 is a perspective view of the ring 60. As shown in fig. 5, a plurality of notches 65 are formed in the ring 60. The cutout 65 is formed to extend axially outward from an axially inner end surface of the ring main body 61.

Fig. 6 is a sectional view of the tapered roller bearing 1 cut by a surface of the cutout 65 formed in the ring 60. As shown in fig. 6, the cutout 65 is also filled with lubricating oil.

The cutout 65 is preferably substantially rectangular in shape having long sides in the axial direction and short sides in the circumferential direction, as shown in fig. 5. The axial length W1 of the cutout 65 is preferably 2 to 10mm, for example. If the axial length W1 of the cutout 65 exceeds 10mm, the sealing performance of the lubricant oil of the holding member 50 may be reduced. The circumferential length W2 of the cutout 65 is preferably 1 to 15mm, for example. If the circumferential length W2 of the cutout 65 exceeds 15mm, foreign matter contained in the cutout 65 may flow out of the cutout 65 again with the flow of the lubricating oil.

As shown in fig. 5, the plurality of cutouts 65 are preferably formed at equal intervals in the circumferential direction. The number of the notches 65 formed in the ring 60 is, for example, 10 to 35.

Fig. 7 is a diagram for explaining the optimum number of cutouts 65 formed in the ring 60. The left drawing of fig. 7 is a sectional view of the holding member 50, and the right drawing is a schematic view when the holding member 50 is viewed from the axial direction. Reference symbol a in fig. 7 denotes a space in which the lubricating oil is stored. The notches 65 are preferably formed so that at least 1 space a in which the lubricating oil is accumulated is present.

In fig. 7, the distance between the central axis L1 and the inner peripheral surface of the ring main body 61 is designated as R. Let r be the distance between the central axis L1 and the end portion on the inner peripheral side of the elastic body lip 70. Let θ be the magnitude of the angle defined by cos θ R/R. Using these R, and θ, an integer n is defined by the following formula (2).

In order to form the cutouts 65 so that at least 1 cutout is present in the space a in which the lubricant is stored, when a plurality of cutouts 65 are formed at equal intervals in the circumferential direction, the number of cutouts 65 may be n or more.

When the inner ring 20 of the tapered roller bearing 1 rotates relative to the outer ring 10, the lubricating oil is stirred. At this time, foreign matter contained in the lubricating oil moves. By forming the cutout 65 in the ring 60, as shown in fig. 6, the foreign matter D enters the cutout 65. Since the inner ring 20 rotates relative to the outer ring 10 in a state where the foreign matter D is accommodated in the cutout 65, the foreign matter D is prevented from being caught between the tapered rollers 30 and the outer ring 10 or between the tapered rollers 30 and the inner ring 20. As a result, the generation of abnormal noise when the inner ring 20 rotates with respect to the outer ring 10 can be suppressed. Further, the life of the tapered roller bearing 1 can be suppressed from being reduced by the foreign matter D.

As is clear from the above description, in the present embodiment, the lubricant retaining member is realized by the thin cylindrical portion 16 and the retaining member 50. The cylindrical portion of the lubricant retaining member is realized by the thin cylindrical portion 16 and the cylindrical portion 52 (ring main body 61). The annular portion of the oil retaining member is realized by the annular portion 51 (the claws 62 and the elastic body lip 70 of the ring 60).

According to the present embodiment, the cutout 65 has a substantially rectangular shape having long sides in the axial direction and short sides in the circumferential direction, as shown in fig. 5. Since the length of the cutout 65 in the circumferential direction is shorter than the length of the cutout 65 in the axial direction, the foreign matter D (see fig. 6) accommodated inside the cutout 65 is prevented from flowing out of the cutout 65 again with the flow of the lubricating oil.

According to the present embodiment, the portion for accommodating the foreign matter D is formed as the cutout 65 penetrating from the inner side to the outer side in the radial direction. This makes it possible to easily form the ring 60 even when the ring 60 is formed of metal.

A modification of embodiment 1 will be described below. The ring 60A of the modification differs from embodiment 1 in that a plurality of holes 66 are formed instead of the plurality of notches 65. Fig. 8 is a perspective view of a ring 60A of a modification.

A hole 66 is formed in an axially intermediate portion of the ring 60A. The hole 66 penetrates from the radially inner side to the radially outer side of the ring 60. Each of the holes 66 is, for example, substantially rectangular in shape.

In the ring 60A of the modification, when the inner ring 20 of the tapered roller bearing 1 rotates relative to the outer ring 10, the lubricating oil is stirred, and foreign matter contained in the lubricating oil moves and is accommodated in the hole 66. At this time, since the hole 66 is surrounded by the ring main body 61 in four directions, the foreign matter accommodated in the hole 66 is less likely to move out of the hole again, as compared with the case of embodiment 1.

In embodiment 1, the cutout 65 is formed in a rectangular shape, but the shape of the cutout 65 is not limited to a rectangular shape. For example, the cutout may have an L-shape. In embodiment 1, the rectangular cutout 65 is formed to have a long side extending in the axial direction, but the arrangement of the cutout is not limited to this. For example, the cutout may be formed obliquely to the axial direction.

However, from the viewpoint of ease of processing for forming the cutout 65 in the ring 60, the shape of the cutout 65 is preferably substantially rectangular.

In embodiment 1 described above, the holding member 50 is configured by the metal ring 60 and the elastic body lip 70, but is not particularly limited thereto. For example, the entire holding member 50 may be made of an elastic body such as rubber.

A tapered roller bearing 1A according to embodiment 2 of the present invention will be described with reference to fig. 9. In the tapered roller bearing 1A, the lubricating oil retaining member is realized by the one end portion 101 in the axial direction of the outer ring 10. Specifically, as described below.

One end 101 of the outer ring 10 in the axial direction includes a cylindrical portion 1011 and an annular portion 1012. This will be explained below.

The cylindrical portion 1011 has a cylindrical shape extending in the axial direction. The cylindrical portion 1011 has an inner peripheral surface 1013. The left end (end on the axial small diameter side) of the inner circumferential surface 1013 is connected to the outer circumferential edge of the step 15.

The annular portion 1012 has an annular shape. The annular portion 1012 extends radially inward from one axial end of the cylindrical portion 1011.

A plurality of grooves 1014, which are a plurality of recesses, are formed in the inner peripheral surface 1013 of the cylindrical portion 1011. The plurality of grooves 1014 are formed at equal intervals in the circumferential direction. The plurality of grooves 1014 each extend in the axial direction. The plurality of grooves 1014 each have a rectangular shape when viewed from the radial direction. In each of the plurality of slots 1014, the length in the axial direction is greater than the length in the circumferential direction.

In the tapered roller bearing 1A, as in the tapered roller bearing 1, foreign matter can be accommodated in the groove 1014. As a result, the occurrence of abnormal noise due to the biting of foreign matter and the reduction in the bearing life can be suppressed.

A tapered roller bearing 1B according to embodiment 3 of the present invention will be described with reference to fig. 10. In the tapered roller bearing 1B, the lubricant retaining member 103 is fixed to one end portion in the axial direction of the outer ring 10B. Specifically, as described below.

An annular step 104 is formed in the circumferential direction on the outer peripheral surface of one end portion in the axial direction of the outer ring 10B. The step 104 is formed on the larger diameter side than the axial center portion of the outer ring 10B. A cylindrical outer peripheral surface 105 extending in the axial direction is formed on the inner peripheral edge of the step 104.

The lubricant retaining member 103 is composed of a ring 103A and an elastic body lip 103B. This will be explained below.

The ring 103A is formed of metal such as stainless steel. The ring 103A includes a cylindrical ring main body 103A1 and an annular claw 103A 2. The claws 103a2 project radially inward from one end (end on the large diameter side) in the axial direction of the ring body 103a 1.

One end portion in the axial direction of the outer ring 10B is press-fitted into the other end portion (end on the smaller diameter side) in the axial direction of the ring main body 103a 1. That is, a part of the inner peripheral surface (a part on the small diameter side) of the ring main body 103a1 contacts the outer peripheral surface 105 formed on the outer ring 10B. In a state where one end portion of the outer ring 10B in the axial direction is press-fitted into the ring body 103a1, the ring body 103a1 contacts the step 104 in the axial direction.

The elastomeric lip 103B is formed of, for example, nitrile rubber or acrylate rubber. The elastomeric lip 103B covers substantially the entirety of the pawl 103a 2. Elastomeric lip 103B includes a cover layer 103B 1. The cover layer 103B1 covers the inner peripheral surface of the ring body 103a 1.

A plurality of grooves 103B2 as a plurality of concave portions are formed in the inner peripheral surface 103B3 of the cover layer 103B 1. The plurality of grooves 103B2 are formed at equal intervals in the circumferential direction. The plurality of grooves 103B2 extend in the axial direction, respectively. The plurality of grooves 103B2 each have a rectangular shape when viewed from the radial direction. In each of the plurality of grooves 103B2, the length in the axial direction is greater than the length in the circumferential direction.

As is clear from the above description, in the embodiment, the ring main body 103a1 and the cover layer 103B1 form a cylindrical portion. The claw 103a2 and the portion of the elastic body lip 103B from which the covering layer 103B1 is removed form a ring-shaped portion.

In the tapered roller bearing 1B, as in the tapered roller bearing 1, foreign matter can be accommodated in the groove 103B 2. As a result, the occurrence of abnormal noise due to the biting of foreign matter and the reduction in the bearing life can be suppressed.

In the tapered roller bearing 1B, a plurality of grooves 103B2 are formed in the cover layer 103B 1. Therefore, the plurality of grooves 103B2 are easily formed.

In the tapered roller bearing 1B, the lubricant retaining member 103 is provided separately from the outer ring 10B. Therefore, the lubricant retaining member 103 is easily formed.

In the tapered roller bearing 1B, the outer ring 10B may not be provided with a thin portion. Therefore, for example, during quenching or conveyance, the outer ring does not crack.

Fig. 11 is an enlarged view of a part of a tapered roller bearing 1B1 according to modification 1 of embodiment 3. In the tapered roller bearing 1B1, the elastomer lip 103B does not include the cover layer 103B 1. In this case, a plurality of grooves 103A3 as a plurality of concave portions are formed in the inner peripheral surface 103a4 of the ring main body 103a 1.

The plurality of grooves 103a3 are formed at equal intervals in the circumferential direction. The plurality of grooves 103a3 each extend in the axial direction. The plurality of grooves 103a3 each have a rectangular shape when viewed from the radial direction. In each of the plurality of grooves 103a3, the length in the axial direction is greater than the length in the circumferential direction.

As is clear from the above description, in the embodiment, the ring main body 103a1 realizes a cylindrical portion. The claw 103a2 and the elastic body lip 103B form a ring-shaped portion.

In the tapered roller bearing 1B1, foreign matter can be accommodated in the groove 103A3, as in the tapered roller bearing 1. As a result, the occurrence of abnormal noise due to the biting of foreign matter and the reduction in the bearing life can be suppressed.

In the tapered roller bearing 1B1, a plurality of grooves 103A3 are formed in the inner peripheral surface 103a4 of the ring main body 103a 1. Therefore, the volume for holding the lubricating oil becomes larger than that of the embodiment (embodiment 3) shown in fig. 10. As a result, more lubricant can be retained.

In the tapered roller bearing 1B1, the lubricant oil retaining member 103 is provided separately from the outer ring 10B. Therefore, the lubricant retaining member 103 is easily formed.

In the tapered roller bearing 1B1, the lubricant oil retaining member 103 is provided separately from the outer ring 10B. Therefore, the thin portion may not be provided in the outer ring 10B. As a result, for example, the outer ring does not crack during quenching and conveyance.

Fig. 12 is an enlarged view of a part of a tapered roller bearing 1B2 according to modification 2 of embodiment 3. The tapered roller bearing 1B2 differs from the tapered roller bearing 1B1 in that the ring 103A is formed of a synthetic resin material. Examples of the synthetic resin material include polyphenylene sulfide (PPS) resin, nylon 46(PA46), nylon 66(PA66), and the like.

In the tapered roller bearing 1B2, foreign matter can be accommodated in the groove 103A3, as in the tapered roller bearing 1. As a result, the occurrence of abnormal noise due to the biting of foreign matter and the reduction in the bearing life can be suppressed.

In the tapered roller bearing 1B2, a plurality of grooves 103A3 are formed in the inner peripheral surface 103a4 of the ring main body 103a 1. Therefore, the volume for holding the lubricating oil becomes larger than that of the embodiment (embodiment 3) shown in fig. 10. As a result, more lubricant can be retained.

In the tapered roller bearing 1B2, a plurality of grooves 103A3 are formed in the ring body 103a 1. Therefore, the plurality of grooves 103a3 are easily formed.

In the tapered roller bearing 1B2, the lubricant oil retaining member 103 is provided separately from the outer ring 10B. Therefore, the lubricant retaining member 103 is easily formed.

In the tapered roller bearing 1B2, the lubricant oil retaining member 103 is provided separately from the outer ring 10B. Therefore, the thin portion may not be provided in the outer ring 10B. As a result, for example, during quenching and conveyance, the outer ring does not crack.

A tapered roller bearing 1C according to embodiment 4 of the present invention will be described with reference to fig. 13. In the tapered roller bearing 1C, the lubricant retaining member 106 is fixed to one end portion in the axial direction of the outer ring 10B, in place of the lubricant retaining member 103, as compared with the tapered roller bearing 1B. Specifically, as described below.

The lubricant retaining member 106 is formed of a synthetic resin material. Examples of the synthetic resin material include polyphenylene sulfide (PPS) resin, nylon 46(PA46), nylon 66(PA66), and the like.

The lubricant retaining member 106 includes a cylindrical portion 1061 and an annular portion 1062. This will be explained below.

The cylindrical portion 1061 has a cylindrical shape extending in the axial direction. The cylindrical portion 1061 has an inner peripheral surface 1063. One end portion in the axial direction of the outer ring 10B is press-fitted into a left end portion (an end on the smaller diameter side in the axial direction) of the inner peripheral surface 1063. That is, a part of the inner peripheral surface 1063 (a part on the smaller diameter side) of the cylindrical portion 1061 contacts the outer peripheral surface 105 formed on the outer ring 10B. In a state where the one end portion of the outer ring 10B in the axial direction is press-fitted into the cylindrical portion 1061, the cylindrical portion 1061 contacts the step 104 in the axial direction.

The annular part 1062 has an annular shape. The annular part 1062 extends radially inward from one end of the cylindrical part 1061 in the axial direction.

A plurality of grooves 1064, which are a plurality of concave portions, are formed in the inner peripheral surface 1063 of the cylindrical portion 1061. The plurality of grooves 1064 are formed at equal intervals in the circumferential direction. The plurality of grooves 1064 extend in the axial direction, respectively. The plurality of slots 1064 each have a rectangular shape when viewed from the radial direction. In each of the plurality of grooves 1064, the length in the axial direction is greater than the length in the circumferential direction.

In the tapered roller bearing 1C, as in the tapered roller bearing 1, foreign matter can be accommodated in the groove 1064. As a result, the occurrence of abnormal noise due to the biting of foreign matter and the reduction in the bearing life can be suppressed.

In the tapered roller bearing 1C, a plurality of grooves 1064 are formed in the cylindrical portion 1061. Therefore, the plurality of grooves 1064 are easily formed.

In the tapered roller bearing 1C, the lubricant retaining member 106 is provided separately from the outer ring 10B. Therefore, the lubricant retaining member 106 is easily formed.

In the tapered roller bearing 1C, the lubricant retaining member 106 is provided separately from the outer ring 10B. Therefore, the thin portion may not be provided in the outer ring 10B. As a result, for example, during quenching and conveyance, the outer ring does not crack.

As described above, the above embodiments are merely examples for carrying out the present invention. Therefore, the present invention is not limited to the above-described embodiments, and the above-described embodiments can be appropriately modified and implemented without departing from the scope of the present invention.

According to the tapered roller bearing according to the embodiment of the present invention, it is possible to suppress the occurrence of abnormal noise and the reduction in the bearing life when one of the inner ring and the outer ring of the bearing rotates relative to the other due to foreign matter contained in the lubricating oil.

Claims

1. A tapered roller bearing is provided with:

an outer ring having a first raceway surface on an inner circumferential surface;

an inner ring having a second raceway surface on an outer circumferential surface thereof and disposed on the same shaft as the outer ring;

a plurality of tapered rollers arranged in a space formed between the first raceway surface and the second raceway surface and arranged in a circumferential direction of the outer ring; and

a lubricant retaining member fixed integrally with the outer ring, wherein,

the lubricant retaining member includes:

a cylindrical portion extending in an axial direction of the outer ring and located at one end portion of the outer ring in the axial direction; and

an annular portion extending inward in a radial direction of the outer ring from one end of the cylindrical portion in the axial direction,

the plurality of recesses are formed in the inner circumferential surface of the cylindrical portion in a circumferentially aligned manner.

2. The tapered roller bearing according to claim 1,

the cylindrical portion is formed of a member different from the outer ring.

3. The tapered roller bearing according to claim 1,

the outer ring includes a thin-walled tube portion formed at one end portion in the axial direction by an annular step provided on the inner peripheral surface and extending in the axial direction,

the cylindrical portion includes:

the thin-walled cylinder portion integrally formed with the outer ring; and

an inner cylindrical portion formed separately from the outer ring, one end of the inner cylindrical portion in the axial direction being connected to an outer peripheral edge of the annular portion, and an outer peripheral surface of the inner cylindrical portion being in contact with an inner peripheral surface of the thin-walled cylindrical portion in the radial direction,

a plurality of notches or holes arranged in the circumferential direction are formed in the inner tube portion,

including the plurality of cutouts or holes to realize the plurality of recesses.

4. The tapered roller bearing according to any one of claims 1 to 3, wherein,

the plurality of recesses each have a substantially rectangular shape when viewed from the radial direction, and a length in the axial direction of the recess is larger than a length in the circumferential direction of the recess.

5. The tapered roller bearing according to any one of claims 1 to 3, wherein,

the plurality of recesses are formed at equal intervals in the circumferential direction,

the number of the plurality of concave portions is n or more satisfying the following formula (1):

in the formula (1), n is an integer, theta is an angle satisfying cos theta as R/R,

wherein R is a radius of an inner peripheral surface of the cylindrical portion, and R is a radius of an inner peripheral edge of the annular portion.

6. The tapered roller bearing according to claim 4,